JP2012188982A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor whose size can be miniaturized without causing a pressure loss in a suction gas passage and accomplishing saving resources, a higher efficiency, and low vibrations.SOLUTION: The rotary compressor includes a compressing mechanism formed in a sealed vessel and driven by a motor through a crankshaft, wherein the compressing mechanism is furnished with a cylinder having an internal space approximately in cylindrical shape where a suction port to suck in the low-pressure fluid in the refrigerating cycle is bored in a radial direction, and a coupling pipe to couple the suction port with a suction pipe located outside the sealed vessel. The cross-section shapes of the suction port, coupling pipe, and suction pipe are non-circular shapes whose dimensions in the rotational direction of the crankshaft are greater than in the axial direction of the crankshaft.

Description

  The present invention relates to a rotary compressor that compresses refrigerant gas used in a refrigeration cycle of a refrigerating and air-conditioning apparatus such as an air conditioner or a refrigerator.

  Conventionally, the length of the cylinder suction port in the circumferential direction of the cylinder is set to be greater than the length of the cylinder in the longitudinal direction, or the length of the suction port in the cylinder longitudinal direction is set to be greater than the length of the cylinder in the circumferential direction. A rotary compressor has been proposed (see, for example, Patent Document 1).

  Also, a suction fitting having a non-circular cross-sectional shape in which the cylinder suction port has a rotational direction dimension larger than the axial direction dimension of the main shaft, one of which is the non-circular cross-sectional shape and the other is a circular cross-sectional shape. There has been proposed a rotary compressor configured to be connected to a suction pipe via a suction pipe (for example, see Patent Document 2).

JP-A-5-99170 JP 2003-214370 A

  In the rotary compressor described in Patent Literature 2, a cylinder suction port having a non-circular cross-sectional shape and a suction pipe having a circular cross-sectional shape are connected via a suction fitting. In order not to cause pressure loss due to the reduction of the flow area between the cylinder suction port and the suction pipe, which is a flow path for low-pressure fluid, the inner diameter of the suction pipe must be made larger than the axial dimension of the suction port, This was an impediment to the realization of downsizing due to the reduction in the axial dimension of the compressor. Further, in the multi-cylinder compressor, the axial interval between the plurality of suction pipes cannot be reduced, and the influence is remarkable.

  The present invention has been made to solve the above-described problems, and can achieve downsizing of the compressor without causing pressure loss of the suction gas flow path, and can achieve resource saving, high efficiency, and low vibration rotation. Provide a compressor.

The rotary compressor according to the present invention includes a compression mechanism that is driven by an electric motor via a crankshaft in a sealed container,
The compression mechanism is
A cylinder having a substantially cylindrical inner space, and a suction port for sucking a low-pressure fluid of the refrigeration cycle is bored in the inner space in a radial direction;
A connecting pipe that connects the suction port and the suction pipe outside the sealed container,
The cross-sectional shapes of the suction port, the connecting pipe, and the suction pipe are non-circular shapes having a rotational dimension larger than the axial dimension of the crankshaft.

  In the rotary compressor according to the present invention, since the cross-sectional shapes of the suction port, the connecting pipe, and the suction pipe are non-circular shapes whose rotational direction dimensions are larger than the axial direction dimensions of the crankshaft, these are compared with the circular cross-sectional shape. Thus, the axial dimensions of the cylinder, connecting pipe, and suction pipe can be reduced without causing pressure loss due to the reduction of the flow path area, and downsizing can be achieved by reducing the axial dimension of the compressor. A resource, high efficiency, and low vibration rotary compressor can be obtained.

FIG. 2 is a diagram showing the first embodiment and is a longitudinal sectional view of a two-cylinder rotary compressor 100. The enlarged view of the compression mechanism 3 of FIG. FIG. 3 is a diagram showing the first embodiment, and is a cross-sectional view of the first cylinder 8. The A section enlarged view of FIG. FIG. 5 shows the first embodiment and is a cross-sectional view of the suction port 50. BB sectional drawing of FIG. FIG. 3 is a diagram showing the first embodiment, and is an external view of a two-cylinder rotary compressor 100 in which suction ports 50 and 51, suction pipes 40 and 41, and connection pipes 60 and 61 have a circular cross-sectional shape. FIG. 3 is a diagram showing the first embodiment, and is an external view of a two-cylinder rotary compressor 100 in which suction ports 50 and 51, suction pipes 40 and 41, and connection pipes 60 and 61 have a non-circular cross-sectional shape. The figure which shows Embodiment 1, and is a figure which shows the connection pipe | tube 60 in case the suction pipe insertion part 60b is circular and the press-fit part 60a is non-circular and it connects with the same flow-path area ((a) is a long hole in a rotation direction, ( b) is an elongated hole in the axial direction). FIG. 5 shows the first embodiment, and is a longitudinal sectional view of a two-cylinder rotary compressor 200 of a first modification. FIG. 5 shows the first embodiment, and is a longitudinal sectional view of a two-cylinder rotary compressor 200 of Modification 1 (the connection pipe connecting portions 22a and 23a of the suction pipes 22 and 23 are non-circular cross-sectional shapes). FIG. 5 shows the first embodiment and is a schematic diagram showing the direction of internal stress of the connecting pipe 60 when the suction port 50 having a long hole and the press-fitting portion 60a of the connecting pipe 60 are press-fitted. FIG. 5 shows the first embodiment, and is a schematic diagram showing a modification of the press-fit portion 60a of the connecting pipe 60. FIG. FIG. 4 shows the first embodiment, and is a cross-sectional view of a press-fit portion 60a of a connecting pipe 60. FIG. 5 shows the first embodiment, and shows a compression process angle θ determined by a suction port edge 50b and a discharge port edge 70a.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view of a two-cylinder rotary compressor 100 showing the first embodiment. The two-cylinder rotary compressor 100 includes an electric motor 2 having a stator 2a and a rotor 2b in a sealed container 1 in a high-pressure atmosphere, a compression mechanism 3 driven by the electric motor 2 via a crankshaft 4, and not shown. Refrigerating machine oil (which lubricates the sliding portion of the compression mechanism 3 and is stored at the bottom of the sealed container 1) is provided.

  The hermetic container 1 includes a body 1a, an upper dish container 1b, and a lower dish container 1c. The upper dish container 1b and the trunk part 1a, and the lower dish container 1c and the trunk part 1a are integrated by welding.

  The compression mechanism 3 is provided at the bottom of the hermetic container 1, and the electric motor 2 is provided above the compression mechanism 3.

  The compression mechanism 3 sucks and compresses low-pressure refrigerant gas from suction pipes 40 and 41 connected to the low-pressure side of the refrigeration cycle.

  The high-pressure refrigerant gas discharged from the compression mechanism 3 passes through the electric motor 2 and is discharged from the discharge pipe 25 to the high-pressure side of the refrigeration cycle.

  The electric motor 2 is usually a brushless DC motor that uses a permanent magnet for the rotor 2b. However, an induction motor may be used.

  Electric power is supplied from an external power source (not shown) to the stator 2 a of the electric motor 2 through the glass terminal 26 and the lead wire 27.

  As will be described later, the suction pipes 40 and 41 are connected to the connection portions 1d and 1e of the sealed container 1 by welding.

  FIG. 2 is an enlarged view of the compression mechanism 3 of FIG. 1, and FIG. 3 is a diagram showing the first embodiment, and is a transverse sectional view of the first cylinder 8. The configuration of the compression mechanism 3 will be described with reference to FIGS. 2 and 3. The crankshaft 4 is fixed to the rotor 2b of the electric motor 2, and is supported by the main bearing 6, the main shaft 4a is provided on the opposite side of the main shaft 4a, the sub shaft 4b is supported by the sub bearing 7, and the main shaft 4a. There are eccentric shafts 4c and 4d formed with a predetermined phase difference (for example, 180 °) between the sub shaft 4b.

  The main bearing 6 has a substantially T-shaped cross section. The main shaft 4a of the crank shaft 4 is fitted with a clearance for sliding, and the main shaft 4a is rotatably supported. Further, one of the opening portions at both ends of the first cylinder 8 (on the electric motor 2 side) is closed.

  The sub bearing 7 has a substantially T-shaped cross section. The countershaft 4b of the crankshaft 4 is fitted with a clearance for sliding and rotatably supports the countershaft 4b. Further, one of the openings at both ends of the second cylinder 9 (on the side opposite to the electric motor 2) is closed.

  The compression mechanism 3 includes a first cylinder 8 on the main shaft 4a side and a second cylinder 9 on the sub shaft 4b side.

  The first cylinder 8 (cylinder) has a substantially cylindrical internal space, and a first piston 11a (also referred to as a rolling piston) that is rotatably fitted to the eccentric shaft 4c of the crankshaft 4 in this internal space. Is provided. Furthermore, the 1st vane 5a which reciprocates in the vane groove | channel 8b is provided, contacting the 1st piston 11a with rotation of the eccentric shaft 4c. The vane groove 8b is provided in the radial direction of the first cylinder 8 and penetrates in the axial direction.

  The axial end faces of the internal space of the first cylinder 8 housing the first piston 11a and the first vane 5a that are rotatably fitted to the eccentric shaft 4c of the crankshaft 4 are connected to the main bearing 6 and the partition plate. 10 is closed to form a sealed chamber 30.

  Further, the chamber 30 includes a suction chamber 30a positioned in front of the rotation direction of the crankshaft 4 (indicated by an arrow in FIG. 3) and a rearward rotation direction of the crankshaft 4 by the first piston 11a and the first vane 5a. And is divided into a compression chamber 30b.

  The second cylinder 9 (cylinder) also has a cylindrical internal space, and a second piston 11b that is rotatably fitted to the eccentric shaft 4d of the crankshaft 4 is provided in this internal space. Further, a second vane (not shown) that reciprocates in a vane groove (not shown) while being in contact with the second piston 11b as the eccentric shaft 4d rotates is provided. The vane groove is provided in the radial direction of the second cylinder 9 and penetrates in the axial direction.

  A second piston 11b that is rotatably fitted to the eccentric shaft 4d of the crankshaft 4 and both axial end surfaces of the inner space of the second cylinder 9 that houses the second vane are connected to the auxiliary bearing 7 and the partition plate 10. And the chamber 31 is formed.

  Furthermore, the chamber 31 is compressed by a suction chamber 31a (not shown) positioned forward in the rotational direction of the crankshaft 4 and a rotational position rearward in the rotational direction of the crankshaft 4 by the second piston 11b and the second vane. It is partitioned into a chamber 31b (not shown).

  The first cylinder 8 and the second cylinder 9 have suction ports 50 and 51 that connect the suction pipes 40 and 41 and the chambers 30 and 31, respectively, so as to suck the low-pressure fluid of the refrigeration cycle into the chambers 30 and 31. It is drilled in the radial direction.

  In addition, connecting pipes 60 and 61 are used to connect (connect) the suction ports 50 and 51 and the suction pipes 40 and 41. The press-fit portions 60a and 61a of the connecting pipes 60 and 61 are press-fitted and connected to press-fit receiving portions 50a and 51a provided on the outside of the suction ports 50 and 51, respectively. The suction pipes 40 and 41 are inserted into the suction pipe insertion portions 60b and 61b of the connection pipes 60 and 61, respectively. The suction pipe insertion parts 60b and 61b are connected to the connection parts 1d and 1e (see FIG. 1) and the suction pipes 40 and 41 of the sealed container 1 by welding.

  The connection portions 1d and 1e of the sealed container 1 are attached perpendicularly to the center line of the sealed container 1 and toward the center of the sealed container 1 so as not to interfere when the connecting pipes 60 and 61 are inserted.

  FIG. 4 is an enlarged view of part A of FIG. The body 1a and the lower dish container 1c of the sealed container 1 are welded together, and the body 1a and the connecting parts 1d and 1e of the sealed container 1 are welded together. For this reason, the connection portion 1d and the connection portion 1e, and the end portion of the body portion 1a of the sealed container 1 and the connection portion 1e are attached with predetermined intervals L1 and L2 so as not to be affected by welding distortion.

  Although not shown, when the sealed container 1 and the lower dish container 1c have an integral structure by drawing or the like, L2 indicates the distance between the end of the sealed container lower part R shape and the connecting portion 1e.

  The low-pressure fluid flowing from the refrigeration cycle is introduced into the chambers 30 and 31 through the suction pipes 40 and 41, the press-fit portions 60a and 61a of the connection pipes 60 and 61, and the suction ports 50 and 51 in this order. Therefore, the cross-sectional areas of the suction pipes 40 and 41, the press-fit portions 60a and 61a of the connection pipes 60 and 61, and the suction ports 50 and 51 are increased in order or substantially the same so that the suction pressure loss does not increase in the suction path of the low-pressure fluid. Yes.

  FIG. 5 shows the first embodiment and is a cross-sectional view of the suction port 50. The suction port 50 has a non-circular cross-sectional shape in which the rotational dimension D is larger than the axial dimension H1 of the crankshaft 4. Accordingly, the axial dimension can be reduced as compared with a circular cross-sectional shape having the same cross-sectional area.

  By setting the suction port 50 to a non-circular cross-sectional shape and satisfying H1 <D, the axial height H of the first cylinder 8 can be set small.

  6 is a cross-sectional view taken along line BB in FIG. As shown in FIG. 6, it is necessary to provide a clearance W between the inner periphery 8a of the first cylinder 8 and the outer periphery 11c of the first piston 11a in order to avoid mutual contact. It is known that the product S of the clearance W and the height H in the axial direction of the first cylinder 8 becomes a leakage flow path that connects the compression chamber 30b and the suction chamber 30a, which causes a reduction in compressor efficiency. . By setting the axial height H of the first cylinder 8 small, the leakage area S can be reduced and the compressor efficiency can be improved.

  As a feature of the present embodiment, the suction pipes 40 and 41 and the connection pipes 60 and 61 also have a non-circular cross section in which the rotational dimension is larger than the axial dimension of the crankshaft 4. Accordingly, the suction pipes 40 and 41 and the connection pipes 60 and 61 can also have a smaller axial height than the circular cross section having the same cross sectional area.

  7 and 8 show the first embodiment. FIG. 7 is an external view of the two-cylinder rotary compressor 100 in which the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a circular cross-sectional shape. FIG. 8 is an external view of the two-cylinder rotary compressor 100 in which the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a noncircular cross-sectional shape.

  In the two-cylinder rotary compressor 100 shown in FIG. 7, the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a circular cross-sectional shape. Further, in the two-cylinder rotary compressor 100 shown in FIG. 8, the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a non-circular cross-sectional shape.

  When the interval L1 between the connecting portion 1d and the connecting portion 1e and the interval L2 between the end of the trunk portion 1a of the sealed container 1 and the connecting portion 1e are constant, the suction ports 50 and 51, the suction pipes 40 and 41, the connecting pipe If the non-circular cross-sections 60 and 61 are formed, the axial distance between the suction pipes 40 and 41 connected to the first cylinder 8 and the second cylinder 9 can be set small, and the axial arrangement of the second cylinder 9 can be set. Can be set low.

  The distance between the axial center of the second cylinder 9 and the lower surface of the lower dish container 1c in the two-cylinder rotary compressor 100 shown in FIG. 7 is K ′, and the second cylinder in the two-cylinder rotary compressor 100 shown in FIG. When the distance between the axial center of 9 and the lower surface of the lower dish container 1c is K, the relationship is K ′> K.

By making the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 into a non-circular cross-sectional shape, the following effects can be obtained.
(1) Since the axial heights of the first cylinder 8 and the second cylinder 9 can be reduced, the axial height dimension of the compressor can be reduced (miniaturization).
(2) Since the suction pipes 40 and 41 and the connecting pipes 60 and 61 are also non-circular cross-sectional shapes, the distance L1 between the connecting portion 1d and the connecting portion 1e, the end of the trunk portion 1a of the sealed container 1 and the connecting portion 1e. The position of the first cylinder 8 and the second cylinder 9 should be lowered as compared with the case where the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 have a circular cross-sectional shape. (Lower vibration by lowering the center of gravity of the compressor).

  On the other hand, even if the suction ports 50 and 51 have a non-circular cross-sectional shape, if the suction pipes 40 and 41 and the connection pipes 60 and 61 are circular, the height of the first cylinder 8 and the second cylinder 9 in the axial direction is high. The height dimension in the axial direction of the compressor cannot be reduced. The outer shape of the two-cylinder rotary compressor 100 in this case is the same as that in FIG. The effect of low vibration due to downsizing of the outer shape of the compressor and low center of gravity cannot be obtained.

  Inside the two-cylinder rotary compressor 100, the axial heights of the first cylinder 8 and the second cylinder 9 are reduced, but the axial centers of the first cylinder 8 and the second cylinder 9 are This is the same as in the case of FIG.

  Compared to the case of FIG. 7, the position of the sub-bearing 7 is increased, the partition plate 10 is thickened, and the position of the main bearing 6 is decreased.

  FIG. 9 is a diagram showing the first embodiment, and is a diagram showing the connecting pipe 60 when the suction pipe inserting portion 60b is circular and the press-fitting portion 60a is non-circular and connected with the same flow path area ((a) is long in the rotation direction. (B) is an elongated hole in the axial direction).

  As shown in FIG. 9, when the suction pipe insertion part 60b of the connecting pipe 60 is circular and the press-fitting part 60a is non-circular and connected with the same flow path area, it always has a reduced diameter part, and suction by low-pressure fluid flow path resistance. Pressure loss is inevitable.

  Therefore, a circular shape having the minimum diameter of the rotational direction dimension (FIG. 9A) of the non-circular suction cross-sectional shape must be selected, but the shape is contrary to the reduction of the compressor axial dimension.

  The effect of this embodiment can be obtained not only in the two-cylinder rotary compressor 100 (FIG. 1) but also in a multi-cylinder compressor. Further, even in a one-cylinder compressor, it is possible to obtain an effect that the height in the cylinder axial direction can be reduced and the axial arrangement of the cylinders can be set low, and the compressor can be reduced in size and vibration can be reduced.

  Furthermore, by making the suction ports 50 and 51, the suction pipes 40 and 41, and the connection pipes 60 and 61 into a noncircular cross-sectional shape, the axial height of the first cylinder 8 and the second cylinder 9 can be reduced. The compressed gas load acting on the eccentric shaft 4c or the eccentric shaft 4d of the crankshaft 4 can be reduced. Furthermore, since the axial heights of the first cylinder 8 and the second cylinder 9 can be reduced, the distance to the main bearing 6 or the sub-bearing 7 serving as a support point for the compressed gas load is reduced, and the crank caused by the compressed gas load is reduced. The bending of the shaft 4 can be suppressed.

  When the deflection of the crankshaft 4 is increased, the inclination of the crankshaft 4 with respect to the main bearing 6 or the sub-bearing 7 is increased, and the bearing reliability is reduced due to contact with each other. It is necessary to ensure rigidity.

  However, since the bending of the crankshaft 4 can be suppressed, a design change that reduces the rigidity of the crankshaft 4 such as the reduction of the shaft diameter is possible, and the efficiency of the compressor can be increased by reducing the shaft sliding loss.

  FIG. 10 shows the first embodiment, and is a longitudinal sectional view of a two-cylinder rotary compressor 200 of the first modification. The difference from the two-cylinder rotary compressor 100 is that an accumulator 20 is provided adjacent to the sealed container 1.

  The accumulator 20 includes an introduction pipe 21 that introduces the low-pressure fluid of the refrigeration cycle to the accumulator 20, and suction pipes 22 and 23 that discharge the low-pressure fluid from the accumulator 20 and are connected to the connection pipes 60 and 61.

  In the rotary compressor, it is desirable to attach the accumulator 20 for uses such as gas-liquid separation of the low-pressure fluid coming from the refrigeration cycle, separation of lubricating oil (refrigeration oil) contained in a small amount in the low-pressure fluid, and noise reduction due to the muffler effect.

  Even when the accumulator 20 is attached, the suction pipes 22 and 23 have a non-circular cross section having a larger rotational dimension than the axial dimension of the crankshaft 4, thereby obtaining the same effect as the two-cylinder rotary compressor 100. be able to.

  However, the cross-sectional shape of the introduction tube 21 of the accumulator 20 is circular. The cross-sectional shape of the piping of the refrigeration cycle equipment is circular, and the basic performance of the compressor that can be easily mounted on a wide variety of refrigeration cycle equipment is satisfied by matching the cross-sectional shape of the introduction pipe 21 to a circular shape.

  The low-pressure fluid coming from the refrigeration cycle passes through the introduction pipe 21 of the accumulator 20, and once flows into the accumulator container 24, and after gas-liquid separation and lubricating oil separation, it flows into the suction pipes 22 and 23. Therefore, the suction pressure loss does not occur due to the difference in cross-sectional shape between the introduction pipe 21 and the suction pipes 22 and 23.

  FIG. 11 is a diagram showing the first embodiment, and is a longitudinal sectional view of the two-cylinder rotary compressor 200 of Modification 1 (the connecting pipe connecting portions 22a and 23a of the suction pipes 22 and 23 are non-circular cross-sectional shapes).

  The suction pipes 22 and 23 of the accumulator 20 may not have the same non-circular cross-sectional shape over the entire length as long as a necessary flow path area can be secured. As shown in FIG. 11, the connecting pipe connecting portions 22a and 23a of the suction pipes 22 and 23 may have a non-circular cross-sectional shape, and the accumulator insertion portions 22b and 23b may have a circular cross-sectional shape. By adopting such a configuration, it is possible to share the parts of the accumulator container 24 with the model in which the suction pipes 22 and 23 are circular.

  Further, the suction pipes 22 and 23 may not be the same part over the entire length. For the suction pipes 22 and 23, a copper material having good weldability and bending formability is generally selected. Considering the recent rise in the market price of copper materials, it is possible to reduce costs by replacing the circular cross-sectional shape portions of the accumulator insertion portions 22b and 23b of the suction pipes 22 and 23 with cheaper materials. .

  The non-circular cross-sectional shapes of the suction ports 50 and 51, the suction pipes 40 and 41 (connecting pipe connecting portions 22a and 23a), and the connecting pipes 60 and 61 are an ellipse, an ellipse, a connection circle, or two circles connected with a short diameter. In any of the shapes, the height in the axial direction can be reduced with respect to the circular cross-sectional shape. Therefore, the suction ports 50 and 51, the suction pipes 40 and 41 (connecting pipe connecting portions 22a and 23a), and the connecting pipe 60 are used. , 61 can be selected as appropriate in consideration of the processing, formability, and the like.

  12 and 13 show the first embodiment, and FIG. 12 shows the direction of internal stress of the connecting pipe 60 when the suction port 50 having a long cross-sectional shape and the press-fit portion 60a of the connecting pipe 60 are press-fitted. FIG. 13 is a schematic diagram showing a modification of the press-fitting portion 60 a of the connecting pipe 60.

  As shown in FIGS. 12 and 13, when a member having a long hole is press-fitted, internal stress generated in the arc portion 60d is transmitted to the flat portion 60c, and the flat portion 60c may be deformed to the inner peripheral side. When the flat part 60c is deformed to the inner peripheral side, the press-fit sealing property of the connecting pipe 60 may decrease, and the refrigerant gas in the high-pressure atmosphere in the sealed container 1 may flow into the suction chamber 30a, leading to a decrease in compressor efficiency. there were.

  FIG. 14 shows the first embodiment, and is a cross-sectional view of the press-fitting portion 60 a of the connecting pipe 60. The press-fit portion 60a of the connecting pipe 60 shown in FIG. 14 has a cross-sectional shape that is a long hole, and a flat portion that connects the two circles of the long hole has a convex shape 60e on the outer peripheral side within the range of the press-fit allowance with the suction port 50. It is what.

  Since the flat portion of the press-fit portion 60a of the connecting pipe 60 has a convex shape 60e on the outer peripheral side, the internal stress generated in the arc portion 60d by the press-fitting is transmitted in a direction to deform the convex shape 60e of the flat portion to the outer peripheral side. Further, it is possible to obtain the connecting pipe 60 without the press-fit sealing performance being lowered without the flat portion being deformed to the inner peripheral side.

  As a method of directing the direction of internal stress transmitted to the flat portion 60c to the outer peripheral side, it is conceivable that the cross-sectional shape is an ellipse, but when comparing the oblong hole and the elliptical shape with the same area and axial dimensions, the elliptical shape However, the direction of rotation is larger than that of the long hole.

  FIG. 15 is a diagram showing the first embodiment and is a diagram showing the compression process angle θ determined by the suction port edge 50b and the discharge port edge 70a.

  As the rotational direction dimension of the suction port 50 increases, as shown in FIG. 15, the suction port edge 50b (Y point, the opposite edge of the first vane 5a), the discharge port edge 70a (Z point, first point) of the discharge port 70. The compression process angle θ determined by the vane 5a on the opposite side of the vane 5a is reduced, and the excluded volume is reduced. ) Is the best choice.

By the way, as problems to the global environment in an air conditioner that uses a refrigerant and operates a refrigeration cycle by the two-cylinder rotary compressors 100 and 200 of the present embodiment, protection of the ozone layer, response to global warming (CO ₂ Etc.), energy conservation, and resource reuse (recycling).

Among these global environmental issues, for the protection of the ozone layer, the refrigerant used is R22 (HFC22), which has a high ozone destruction coefficient, and R410A (HFC32: HFC125 = 50: 50 (weight ratio)) where the ozone destruction coefficient is zero. The air conditioner switched to) has already been commercialized. Incidentally, HFC125 is a chemical formula _CHF 2 -CF ₃ (chemical name pentafluoroethane).

On the other hand, the demand for global warming prevention measures is increasing. In an air conditioner, evaluation is performed using a global warming index called a total equivalent warming impact (TEWI). This TEWI is the CO ₂ that is emitted to produce the energy consumed when producing the materials that make up the air conditioner, as well as the effects (direct effects) due to the atmospheric release of the refrigerant and the energy consumption (indirect effects) of the device. It is expressed as the sum of

  For the calculation of TEWI, the global warming potential GWP (Global Warming Potential) of refrigerant, the amount of refrigerant, and the annual energy consumption efficiency APF (Annual Performance Factor) representing the efficiency of the air conditioner are used. In order to prevent global warming, it is necessary to select a refrigerant having a small GWP value and a large APF value in order to reduce the TEWI value.

  Currently used R410A has a GWP of 2090, which is larger than the conventionally used R22 of 1810. Therefore, in order to prevent global warming, hydrocarbon-based R290 has been developed as a refrigerant with a GWP value of zero, and HFO1234yf has been developed as a low GWP refrigerant with a GWP of 50 or less. However, there are problems with flammability and energy saving. Therefore, R32 (HFC32) is cited as a candidate as a refrigerant having a relatively low GWP.

  The GWP value of R32 is 675, which is about 1/3 of the GWP value of R22 and R410A, and can reduce the impact on global warming. Therefore, when using R32, it is necessary to reduce the amount of refrigerant.

As for energy saving, CO ₂ is indirectly discharged by power consumption when the air conditioner is operated. Therefore, the performance of the air conditioner is enhanced to save energy, thereby contributing to the prevention of global warming.

In home air conditioners, the proportion of indirect CO ₂ emissions due to power consumption during use accounts for a large proportion. Therefore, by promoting energy saving, it is possible to reduce CO ₂ emissions. When R32 is used as the refrigerant, it is not a low GWP refrigerant as described above. Therefore, in order to reduce the influence on global warming, it is necessary to reduce the amount of refrigerant while simultaneously realizing energy saving.

  DESCRIPTION OF SYMBOLS 1 Airtight container, 1a trunk | drum, 1b upper plate container, 1c lower plate container, 1d connection part, 1e connection part, 2 motor, 2a stator, 2b rotor, 3 compression mechanism, 4 crankshaft, 4a main shaft, 4b sub Shaft, 4c eccentric shaft, 4d eccentric shaft, 5a first vane, 6 main bearing, 7 auxiliary bearing, 8 first cylinder, 8b vane groove, 9 second cylinder, 10 partition plate, 11a first Piston, 11b 2nd piston, 11c outer circumference, 20 accumulator, 22 suction pipe, 22a connection pipe connection part, 23 suction pipe, 23a connection pipe connection part, 25 discharge pipe, 26 glass terminal, 27 lead wire, 30 chamber, 30a Suction chamber, 30b Compression chamber, 31 chamber, 31a Suction chamber, 31b Compression chamber, 40 Suction pipe, 41 Suction pipe, 50 Suction port, 50a Press-in receiving part, 50b Suction port edge 51 suction port, 51a press-fitting receiving part, 60 connecting pipe, 60a press-fitting part, 60b suction pipe inserting part, 60c flat part, 60d arc part, 60e convex shape, 61 connecting pipe, 61a press-fitting part, 61b suction pipe inserting part, 70 Discharge port, 70a Discharge port edge, 100 2-cylinder rotary compressor, 200 2-cylinder rotary compressor.

Claims (5)

Provided with a compression mechanism driven by an electric motor through a crankshaft in a sealed container,
The compression mechanism is
A cylinder having a substantially cylindrical inner space, in which a suction port for sucking a low-pressure fluid of a refrigeration cycle is formed in the inner space in a radial direction;
A connecting pipe that connects the suction port and a suction pipe outside the sealed container;
A rotary compressor characterized in that cross-sectional shapes of the suction port, the connecting pipe, and the suction pipe are non-circular shapes having a rotational dimension larger than an axial dimension of the crankshaft. An accumulator, an introduction pipe for introducing a low-pressure fluid into the accumulator, and the suction pipe connected to the connection pipe by discharging the low-pressure fluid from the accumulator,
2. The rotary compressor according to claim 1, wherein a cross-sectional shape of the suction pipe is a non-circular shape having a rotational direction dimension larger than an axial dimension of the crankshaft, and the cross-sectional shape of the introduction pipe is a circular shape. . An accumulator, an introduction pipe for introducing a low-pressure fluid into the accumulator, and the suction pipe connected to the connection pipe by discharging the low-pressure fluid from the accumulator,
The cross-sectional shape of the connecting pipe connecting portion of the suction pipe is a non-circular shape whose rotational direction dimension is larger than the axial dimension of the crankshaft, and the cross-sectional shape of the accumulator insertion portion of the suction pipe is a circular shape, The rotary compressor according to claim 1, wherein the cross-sectional shape of the rotary compressor is a circular shape.   The rotation according to any one of claims 1 to 3, wherein the noncircular cross-sectional shape is any one of an ellipse, an ellipse, a connection circle, or a shape formed by connecting two circles with a short diameter. Compressor.   The non-circular cross-sectional shape of the connecting pipe that is press-fitted into the suction port is a long hole, and a flat portion that connects two circles of the long hole is disposed on the outer peripheral side within the range of the press-fitting allowance between the suction port and the connecting pipe. The rotary compressor according to any one of claims 1 to 3, wherein the rotary compressor has a convex shape.

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